EP0188101B1 - Hydraulisches Motorlagerungssystem - Google Patents

Hydraulisches Motorlagerungssystem Download PDF

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Publication number
EP0188101B1
EP0188101B1 EP85309105A EP85309105A EP0188101B1 EP 0188101 B1 EP0188101 B1 EP 0188101B1 EP 85309105 A EP85309105 A EP 85309105A EP 85309105 A EP85309105 A EP 85309105A EP 0188101 B1 EP0188101 B1 EP 0188101B1
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EP
European Patent Office
Prior art keywords
mounting system
accordance
chamber
resilient
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85309105A
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English (en)
French (fr)
Other versions
EP0188101A1 (de
Inventor
Kenichi Watanabe
Haruyuki No. 915 Mazda's Taniguchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mazda Motor Corp
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Mazda Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP26885184A external-priority patent/JPS61146629A/ja
Priority claimed from JP26884784A external-priority patent/JPS61146625A/ja
Priority claimed from JP59268846A external-priority patent/JPH0637133B2/ja
Priority claimed from JP26884984A external-priority patent/JPS61146627A/ja
Priority claimed from JP60068306A external-priority patent/JPH0637138B2/ja
Application filed by Mazda Motor Corp filed Critical Mazda Motor Corp
Publication of EP0188101A1 publication Critical patent/EP0188101A1/de
Application granted granted Critical
Publication of EP0188101B1 publication Critical patent/EP0188101B1/de
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/26—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper characterised by adjusting or regulating devices responsive to exterior conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like

Definitions

  • the present invention relates to hydraulic mounting systems for power units such as engines. More specifically, the present invention pertains to a mounting system for a power unit having an output shaft, the mounting system including hydraulic mounting units located at the opposite sides of the power unit output shaft for supporting the power unit on a base, the units having hydraulic chamber means connected together by conduit means, each unit including resilient means between the power unit and base to provide a resilient support for the power unit, and the hydraulic chamber means being provided beneath the resilient means to apply a hydraulic pressure to the resilient means.
  • a mounting system for a power unit having an output shaft the mounting system including hydraulic mounting units located at the opposite sides of the power unit output shaft for supporting the power unit on a base, the units having hydraulic chamber means connected together by conduit means, each unit including resilient means between the power unit and base to provide a resilient support for the power unit, and the hydraulic chamber means being provided beneath the resilient means to apply a hydraulic pressure to the resilient means.
  • the U.S. patent 2,705,118 issued to M.G. Beck on March 29, 1955 discloses a resilient mounting system which includes a pair of mounting units located at the opposite sides of the output shaft of an engine and each having a rubber mount provided at a lower side with a hydraulic chamber.
  • the hydraulic chamber of one mounting unit is connected with the hydraulic chamber of the other mounting unit through a conduit which may be provided with an orifice so that torsional vibrations are absorbed by the damping effect c f the orifice.
  • the proposal is intended to provide an essentially rigid support insofar as the vertical translation is concerned but to make the torsional or rolling spring coefficient of the mounting system relatively small.
  • Another object of the invention is to provide power unit mounting means in which the rolling spring coefficient can be maintained in a relatively low range throughout the operation of the power unit.
  • a mounting system for a power unit having an output shaft comprising hydraulic mounting units located at the opposite sides of the output shaft for supporting the power unit on a base, the mounting units having hydraulic chamber means connected together by conduit means, each unit including resilient means between the power unit and base to provide a resilient support for the power unit, and the hydraulic chamber means being provided beneath the resilient means to apply a hydraulic pressure to the resilient means;
  • connection together of the hydraulic chamber means of the mounting units by the conduit means makes it possible in general to decrease the rolling spring coefficient of the mounting system.
  • the resilient wall means are deflected under the hydraulic pressure to vary the volumes of the hydraulic chamber means so that it is possible to maintain the rolling rigidity low.
  • each mounting unit with back-up pressure chamber means at a side of the resilient means opposite to the hydraulic chamber means, the back-up pressure chamber means being opened to the atmosphere through orifice means.
  • the back-up pressure chamber means functions to suppress rapid deflections of the resilient wall means which may otherwise occur under bouncing of the vehicle equipped with the power unit.
  • FIG. 1 there is shown a vehicle engine mounting system with which an engine 2 having an output shaft 2a is mounted on a vehicle body 1.
  • the engine 2 has mounting arms 3 extending in the opposite directions from the output shaft 2a.
  • Each of the mounting arms 3 is supported through a mounting unit 4 on the vehicle body 1.
  • the mounting unit 4 includes a mounting rubber 6 attached to one end of a cylindrical case 5 which is secured at the other end to the vehicle body 1.
  • the mounting rubber 6 is connected by means of a bolt 9 with the mounting arm 3.
  • a resilient membrane 7 to define a hydraulic chamber 8 in the casing 5 between the mounting rubber 6 and the membrane 7.
  • the hydraulic chamber 8 is filled with non-compressible hydraulic liquid.
  • a stopper plate 11 for limiting the movement of the membrane 7.
  • the stopper plate 11 is formed with a plurality of perforations 13 to allow free flow through the plate 11.
  • the hydraulic chambers 8 are connected together by a conduit 10 which is provided with an orifice 15.
  • the rolling spring coefficient of the mounting system changes as shown by a broken line A in Figure 2 as already described. It will therefore be noted that the rolling spring coefficient increases significantly under the frequency fn.
  • the rolling spring coefficient can be maintained substantially constant as shown by a solid line B in Figure 2. It is therefore possible to maintain the rolling spring coefficient at a relatively low value.
  • the resilient membranes 7 are deflected until they abut to either the plate 11 or 12 since there will be a certain delay in the fluid flow through the conduit 10. Thereafter, the membranes 7 are gradually returned to their neutral positions.
  • the rolling rigidity is momentarily increased to prevent excessive rolling of the engine.
  • the orifice 15 in the conduit 10 facilitates the aforementioned function by resisting the fluid flow through the conduit 10.
  • FIG. 4 shows another embodiment of the present invention
  • the embodiment shown therein is substantially the same as the previous embodiment except that the orifice 15 in the previous embodiment is substituted by a solenoid valve 16 which includes a valve casing 17 having a valve seat 17a and a valve member 18 adapted for engagement with the valve seat 17a.
  • the valve member 18 is urged by means of a spring 18a toward an open position and a solenoid 19 is provided for forcing the valve member 18 toward a closed position when energized.
  • the arrangement is such that the valve member 18 is forced firmly toward the valve seat 17a when the valve member 18 is in the closed position under the hydraulic pressure produced by the reaction force of the forward tractive torque of the engine 2.
  • FIG. 5 which shows a further embodimnt of the present invention
  • the embodiment shown therein is different from the embodiment shown in Figure 4 in that the conduit 10 is connected with the hydraulic chambers 8 through passages 9'a formed in the bolts 9' connecting the mounting arms 3 with the mounting rubbers 6.
  • the arrangement is suitable for a structure wherein the solenoid valve 16 is mounted on the body of the engine 2.
  • FIG 6 shows a still further embodiment of the present invention.
  • the air chamber 14 defined by the dish-shaped plate 12 is opened to the atmosphere through an orifice 20 formed in the plate 12.
  • the orifice 20 provides a damping effect to the movement of the resilient membrane 7.
  • the plate 12 is provided with a valve 21 in addition to the orifice 20.
  • the valve 21 is constituted by a pair of spaced apart, per f orated plates 22 and a floating valve plate 23 disposed between the perforated plates 22.
  • the embodiment shown therein includes a solenoid operated stopper 30 for constraining movement of the membrane 7.
  • the stopper 30 is mounted on the dish-shaped plate 12 defining the air chamber 14 and includes a stopper plate 31 located in the air chamber 14.
  • the stopper plate 31 is attached to a push rod 31a which extends outwardly through the plate 12.
  • a solenoid 32 is mounted on the plate 12 to encircle the push rod 31a. When the solenoid 32 is de-energized, the stopper plate 31 is in the position shown in Figure 8 but, when the solenoid 32 is energized, the stopper plate 31 is moved upward to constrain the movement of the membrane 7.
  • the stopper plate 11 in the hydraulic chamber 8 is formed with an orifice 33 and a valve 34.
  • the valve 34 includes a perforated plate 35 attached to the stopper plate 11 with a spacing therebetween.
  • the stopper plate 11 is formed with perforations in the area surrounded by the plate 35. In the space between the plates 11 and 35, there is a floating valve member 36.
  • the valve 34 functions in the same manner as the valve 21 in the previous embodiment does.
  • the membrane 7 When the solenoid 32 is de-energized, the membrane 7 is free to deflect and the hydraulic fluid flows through the orifice 33 and the valve 34 as long as the vertical movement of the engine 2 is slow. However, when the vertical movement is fast, the valve 34 is closed to allow the hydraulic fluid flow only through the orifice 33. Thus, the vertical oscillation of the engine 2 is absorbed due to the flow resistance provided by the orifice 33.
  • the stopper plate 31 prevents the downward movement of the membrane 7.
  • the hydraulic pressure in the chamber 8 may tend to depress the membrane 7 and the stopper plate 31 downward.
  • the aforementioned orifice 33 and the valve 34 function to prevent a high pressure from being transmitted through the stopper plate 11. Thus, the stopper plate 31 is not subjected to a strong downward force so that it is unnecessary to increase the energizing current to the solenoid 32.
  • FIG. 9 there is shown a further embodiment which includes an auxiliary hydraulic chamber 50 connected through a passage 51 with the main hydraulic chamber 8.
  • the resilient membrane 7 is not located in the main chamber 8 but in the auxiliary chamber 50.
  • a dish-shaped plate 12 is provided as in the embodiment of Figure 1 to define a closed air space 14 beneath the membrane 7.
  • a perforated stopper plate 11 is provided above the membrane as in the previous embodiments.
  • a solenoid operated shut-off valve 52 is provided in the passage 51. The solenoid valve 52 closes the passage 51 when energized.
  • a second solenoid valve 53 which closes the conduit 10 when energized.
  • the conduit 10 is provided with a bypass passage 54 which bypasses the solenoid valve 53.
  • the bypass passage 54 there is an enlarged chamber 55 which is provided with a resilient membrane or diaphragm 56.
  • tne rolling spring coefficient of the mounting system is substantially constant as shown by a line a in Figure 10. Since the auxiliary chamber 50 is in communication with the main chamber 8, the membrane 7 in the auxiliary chamber 50 can deflect under the pressure change in the main chamber 8.
  • the rolling spring coefficient is substantially constant but the value of the spring is larger than in the case where the solenoid valves 52 and 53 are both opened. This is because the resiliency of the membrane 56 has an influence on the spring coefficient, as shown by the line y.
  • the rolling spring coefficient changes as shown by a line 5.
  • the line 5 is similar to the line ⁇ but shifted to the right due to the influence of the membrane 56.
  • a control unit 100 is provided to control the operation of the valves 52 and 53 in accordance with the frequency of the rolling oscillation.
  • the valve 52 is closed under the frequency lower than the value f2 at which the line 6 intersects the line a.
  • the valve 53 is closed under the frequency fl and f2, the value fl being the frequency at which the lines (3 and cross each other. With this control, the rolling spring coefficient changes as shown by a thick line in Figure 10.
  • the dish-shaped plate 12 for defining the air chamber 14 is provided with a pneumatically operated stopper 60.
  • the stopper 60 includes an opening 61 formed in the plate 12 and a stopper member 62 for limiting the movement of the membrane 7.
  • the member 62 is connected with a stem 63 which is connected with a diaphragm 64 of a pneumatic actuator 65.
  • the actuator 65 has first and second chambers 66 and 67 formed at the opposite sides of the diaphragm 64.
  • a spring 68 is provided for biasing the member 62 toward a lowered position.
  • the chamber 66 which is closer to the plate 12 is connected through a line 69 and a check valve 70 with a vacuum tank 71 which is in turn connected with a vacuum pump 72.
  • the suction pressure introduced into the chamber 66 functions to force the member 62 toward a raised position.
  • the chamber 67 which is further from the plate 12 is connected through a line 73 with a solenoid valve 74.
  • the solenoid valve 74 functions to connect the line 73 alternately with a line 75 or a line 76.
  • the line 75 is connected through the check valve 70 with the vacuum tank 71.
  • the line 76 is opened through a screen 77 to the atmosphere.
  • a pneumatically operated valve 80 which includes a valve seat 81 and a valve member 82 for cooperation with the valve seat 81.
  • the valve member 82 is connected with a valve stem 83 which is in turn connected with a diaphragm 84 of a pneumatic actuator 85.
  • the pneumatic actuator 85 has suction pressure chambers 86 and 87 which are provided at the opposite sides of the diaphragm 84.
  • a spring 88 is provided to force the valve member 82 toward a closed position.
  • the chamber 86 is connected with the line 69 so that it is continuously supplied with the suction pressure which functions to force the valve member 82 toward an open position.
  • the chamber 87 is connected through a line 89 with a solenoid valve 90 which functions to connect the line 89 alternately with a line 91 or a line 92.
  • the line 91 is connected through the check valve 70 with the vacuum tank 71.
  • the line 92 is opened to the atmosphere through the screen 77.
  • a controller 93 which may be constituted by a microprocessor.
  • the vehicle equipped with the engine 2 is provided with an engine throttle valve position detector 94 for detecting the position of the engine control foot pedal (not shown), a transmission position detector 95 for detecting the position of the transmission (not shown), a vehicle speed detector 96 for detecting the vehicle running speed and a clutch condition detector 97 for detecting that the clutch (not shown) is in engagement.
  • the engine 2 is provided with an engine speed detector 98 and an engine roughness detector 99. The signals from the detectors are applied to the controller 93 which then interprets the vehicle operating condition.
  • the controller 93 When it is judged that the engine output torque is not high and the engine rolling oscillation is of a frequency which is higher than the frequency fO where the line A in Figure 2 intersects the line K, the controller 93 produces a signal to energize the solenoid valve 90 to open the chamber 87 to the atmosphere so that the valve 80 is opened. At the same time the solenoid valve 74 is de-energized and the chambers 67 of the actuators 65 are connected with the vacuum tank 71. Thus, the stoppers 60 are lowered. Therefore, the membrane 7 becomes free to move so that the rolling spring coefficient becomes substantially constant as shown by the line B in Figure 2.
  • the controller 93 produces a signal to energize the solenoid valve 74 so that the chambers 67 are opened to the atmosphere.
  • the stopper members 62 are raised to constrain the membrane 7.
  • the rolling spring coefficient then changes as shown by the line A in Figure 2.
  • the solenoid valve 90 When it is judged that the engine output torque is high, the solenoid valve 90 is energized to connect the chamber 87 with the vacuum tank 71. Therefore, the valve 80 in the conduit 10 is closed. If the stopper member 62 is in the lowered position, the membrane 7 is free to deflect so that the rolling oscillation is resisted by the deflections of the mounting rubber 6 and the membrane 7. If the stopper member 62 is in the raised position, the rolling rigidity can be further increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Claims (19)

1. Tragwerk für ein Triebwerk (2) mit einer Abtriebswelle (2a), wobei das Tragwerk auf entgegengesetzten Seiten der Abtriebswelle (2a) angeordnete hydraulische Trageinheiten (4) zum Abstützen des Triebwerks (2) auf einer Basis (1) aufweist, die Trageinheiten (4) Hydraulikkammermittel (8) besitzen, die durch Leitungsmittel (10) miteinander verbunden sind, jede Einheit (4) zwischen dem Triebwerk (2) und der Basis (1) angeordnete, elastische Mittel (6) zum elastischen Abstützen des Triebwerks (2) aufweist und die Hydraulikkammermittel (8) unter den elastischen Mitteln (6) angeordnet sind und dazu dienen, auf die elastischen Mittel (6) einen hydraulischen Druck auszuüben, dadurch gekennzeichnet, daß die Hydraulikkammermittel (8) in jeder der Trageinheiten (4) mindestens teilweise von elastischen Wandmitteln (7) begrenzt sind, die unter dem hydraulischen Druck in dem Kammermittel (8) auslenkbar sind.
2. Tragwerk nach Anspruch 1, gekennzeichnet durch Bewegungsbeschränkungsmittel (30, 60), die wahlweise in eine Bewegungsbeschränkungsstellung bewegbar sind, in der die Bewegungsbeschränkungsmittel (30, 60) die Auslenkung der elastischen Wandmittel (7) beschränken.
3. Tragwerk nach Anspruch 2 mit einer Einrichtung (31a, 32, 65) zum Bewegen der Bewegungsbeschränkungsmittel (30, 60) in die Bewegungsbeschränkungsstellung bei niedriger Rollfrequenz.
4. Tragwerk nach Anspruch 1, dadurch gekennzeichnet, daß die Hydraulikkammermittel (4) eine erste Kammer (8) aufweisen sowie eine zweite Kammer (50), die mit der ersten Kammer (8) durch Drosselmittel (51, 52) verbunden sind, wobei die elastischen Wandmittel (7) den zweiten Kammermitteln (50) zugekehrt sind und die Leitungsmittel (10) in die erste Kammer (8) münden.
5. Tragwerk nach Anspruch 4, dadurch gekennzeichnet, daß die Drosselmittel Ventilmittel (52) aufweisen, die parallel zu einer Drosselblende (51) zwischen der ersten und der zweiten Kammer (8, 50) angeordnet sind und bei einem hohen Druckunterschied zwischen der ersten und der zweiten Kammer (8, 50) schließen.
6. Tragwerk nach Anspruch 3, dadurch gekennzeichnet, daß die Bewegungsmittel Elektromagnetmittel (31 a, 32) umfassen.
7. Tragwerk nach Anspruch 3, dadurch gekennzeichnet, daß die Bewegungsmittel pneumatische Betätigungsmittel (65) umfassen.
8. Tragwerk nach Anspruch 2, dadurch gekennzeichnet, daß das Leitungsmittel (10) mit Ventilmitteln (16, 80) zum Schließen der Leitungsmittel (10) versehen sind.
9. Tragwerk nach Anspruch 8 mit einer elektrischen Steuerung (93) zum Betätigen der Führungsmittel (62, 65) in Abhängigkeit von dem Betriebszustand des Triebwerks (2).
10. Tragwerk nach Anspruch 1 mit ersten Anschlagmitteln (12, 14) zum Begrenzen der Auslenkung der elastischen Wandmittel (7) in der Richtung einer Vergrößerung des Volumens der Hydraulikkammermittel (8) und zweite Anschlagmittel (11) zum Begrenzen der Auslenkung der elastischen Wandmittel (7) in der entgegengesetzten Richtung.
11. Tragwerk nach Anspruch 10, dadurch gekennzeichnet, daß die ersten Anschlagmittel eine mit mindestens einem Loch (13) ausgebildete Anschlagplatte (11) aufweisen.
12. Tragwerk nach Anspruch 10 oder 11, dadurch gekennzeichnet, daß die zweiten Anschlagmittel eine Platte (12) aufweisen, die einen zwischen den elastischen Wandmitteln (7) und der Platte (12) angeordneten, geschlossenen Luftraum (14) umfassen.
13. Tragwerk nach einem der Ansprüche 10 bis 12, dadurch gekennzeichnet, daß die Leitungsmittel (10) mit Drosselblendenmitteln (15) versehen sind.
14. Tragwerk nach Anspruch 1 oder einem der Ansprüche 10 bis 12, dadurch gekennzeichnet, daß jede Trageinheit (4) den Hydraulikkammermitteln (8) zugekehrte, elastische Mittel (6) besitzt, die mit dem Triebwerk (2) durch Verbindungsbolzenmittel (9') verbunden sind, die mit den sie durchsetzenden Leitungsmitteln (10) ausgebildet sind.
15. Tragwerk nach Anspruch 11, dadurch gekennzeichnet, daß die zweiten Anschlagmittel eine Platte (12) umfassen, die einen zwischen den elastischen Wandmitteln (7) und der Platte (12) angeordneten Luftraum (14) begrenzt und die Drosselblendenmittel (20) aufweist, durch die hindurch der Luftraum (14) zu der Atmosphäre hin offen ist.
16. Tragwerk nach Anspruch 15, dadurch gekennzeichnet, daß die Platte (12) der zweiten Anschlagmittel den Drosselblendenmitteln (20) parallelgeschaltete Ventilmittel (21) aufweist, die bei einer hohen Druckdifferenz zwischen dem Luftraum (14) und der Atmosphäre schließen.
17. Tragwerk nach Anspruch 1, dadurch gekennzeichnet, daß die Hydraulikkammermittel eine Hauptkammer (8) und eine Hilfskammer (50) umfassen, die durch Leitungsmittel (51) miteinander verbunden sind, daß die elastischen Wandmittel (7) der Hilfskammer (50) zugekehrt sind, daß in den Leitungsmitteln (51) Ventilmittel (52) vorgesehen sind und daß die elastischen Mittel (6) der Hauptkammer (8) zugekehrt sind und das Triebwerk (2) tragen.
18. Tragwerk nach Anspruch 17 mit Mitteln (100) zum Schließen der Ventilmittel (52) bei Rollschwingungen in einem niedrigen Frequenzbereich.
19. Tragwerk nach Anspruch 17 oder 18, dadurch gekennzeichnet, daß die Leitungsmittel (10) mit Ventilmitteln (53) und die Ventilmittel (53) umgehenden Umgehungskanalmitteln (54) versehen und in den Umgehungskanalmitteln (54) zweite elastische Wandmittel (56) vorgesehen sind.
EP85309105A 1984-12-19 1985-12-13 Hydraulisches Motorlagerungssystem Expired EP0188101B1 (de)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP26885184A JPS61146629A (ja) 1984-12-19 1984-12-19 パワ−ユニツトのマウンテイング装置
JP26884784A JPS61146625A (ja) 1984-12-19 1984-12-19 パワ−ユニツトのマウンテイング装置
JP268847/84 1984-12-19
JP59268846A JPH0637133B2 (ja) 1984-12-19 1984-12-19 パワ−ユニツトのマウンテイング装置
JP268846/84 1984-12-19
JP26884984A JPS61146627A (ja) 1984-12-19 1984-12-19 パワ−ユニツトのマウンテイング装置
JP268851/84 1984-12-19
JP268849/84 1984-12-19
JP68306/85 1985-03-30
JP60068306A JPH0637138B2 (ja) 1985-03-30 1985-03-30 パワ−ユニツトのマウンテイング装置

Publications (2)

Publication Number Publication Date
EP0188101A1 EP0188101A1 (de) 1986-07-23
EP0188101B1 true EP0188101B1 (de) 1989-03-15

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EP85309105A Expired EP0188101B1 (de) 1984-12-19 1985-12-13 Hydraulisches Motorlagerungssystem

Country Status (3)

Country Link
US (1) US4706945A (de)
EP (1) EP0188101B1 (de)
DE (1) DE3568744D1 (de)

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JPS6054537B2 (ja) * 1980-10-09 1985-11-30 東洋ゴム工業株式会社 空気減衰付ゴム支承装置
US4505461A (en) * 1980-12-03 1985-03-19 Nissan Motor Company, Limited Fluid-filled engine mount device
JPS57191127A (en) * 1981-05-18 1982-11-24 Nissan Motor Co Ltd Engine mount filled with fluid
JPS58104447U (ja) * 1982-01-08 1983-07-15 日産自動車株式会社 パワ−ユニツトのマウンテイング装置
JPS59122447U (ja) * 1983-02-04 1984-08-17 トヨタ自動車株式会社 防振ゴム装置
GB2135795B (en) * 1983-02-09 1987-12-16 Mitsubishi Motors Corp A rolling control apparatus for an engine
US4595183A (en) * 1983-03-09 1986-06-17 Bridgestone Tire Company Limited Vibration isolating device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19853620C2 (de) * 1997-11-20 2001-10-31 Toyoda Gosei Kk Schwingungsisolationssystem der flüssigkeitsdichten Bauart

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DE3568744D1 (en) 1989-04-20
EP0188101A1 (de) 1986-07-23
US4706945A (en) 1987-11-17

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